WO2010121450A1 - Cylindre rotatif continu de type a ailettes - Google Patents

Cylindre rotatif continu de type a ailettes Download PDF

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Publication number
WO2010121450A1
WO2010121450A1 PCT/CN2009/072971 CN2009072971W WO2010121450A1 WO 2010121450 A1 WO2010121450 A1 WO 2010121450A1 CN 2009072971 W CN2009072971 W CN 2009072971W WO 2010121450 A1 WO2010121450 A1 WO 2010121450A1
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WO
WIPO (PCT)
Prior art keywords
cam
angle
rotor
blade
annular chamber
Prior art date
Application number
PCT/CN2009/072971
Other languages
English (en)
Chinese (zh)
Inventor
周华
Original Assignee
Zhou Hua
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Zhou Hua filed Critical Zhou Hua
Publication of WO2010121450A1 publication Critical patent/WO2010121450A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/40—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/08 or F04C2/22 and having a hinged member
    • F04C2/44—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/08 or F04C2/22 and having a hinged member with vanes hinged to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C9/00—Oscillating-piston machines or pumps
    • F04C9/002—Oscillating-piston machines or pumps the piston oscillating around a fixed axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings

Definitions

  • the present invention relates to a piston cylinder.
  • crankshaft connecting rod piston mechanisms turbine mechanisms and vane motor mechanisms that are positive (reverse) to the mechanism for converting fluid pressure energy and mechanical energy in a continuous circular rotation motion.
  • the main shortcomings are non-uniform speed, non-equal torque, non-continuous power output, inertial impact, dead point, leading to multi-level misalignment of related machines, large vibration, high noise, low efficiency,
  • the work frequency is low, the structure is complicated, and the processing is difficult.
  • Turbine mechanism which is characterized by the conversion process of fluid kinetic energy in the middle of the positive (reverse) direction conversion process of fluid pressure energy and mechanical energy.
  • the main disadvantages are large conversion loss, low efficiency, large volume and high material requirements. , high processing difficulty and low life.
  • the blade motor mechanism is characterized by eccentric rotation.
  • the main disadvantages are non-equal speed, non-equal torque, non-continuous power output, difficult sealing, low output power, low efficiency, high noise, and easy vibration.
  • a vane type swing cylinder relating to the present invention has a structure as shown in Fig. 12: a cylinder 100, a rotor 200
  • the partition plate 300, the working medium inlet and outlet 400 and 500, and the vane 700 are composed; the cylinder block 100 and the rotor 200 constitute an annular chamber, and the continuous cavity of the annular chamber is partitioned by the partition plate 300, and the two working medium inlets and exits are separated from the partition plate.
  • the vane 700 divides the annular chamber into two working chambers, and under the action of the external reversing valve, respectively, the pressure working medium and the atmospheric circuit are respectively connected, and the pressure difference between the two chambers generates torque on the vane to push the rotor to rotate. Because the displacement of the diaphragm, the stroke of the blade rotation is generally lower than 280 degrees, so it is generally used for the reciprocating oscillating motion output mechanism.
  • An object of the present invention is to provide a vane type continuous rotary cylinder.
  • the present invention provides a vane type continuous rotary cylinder including a cylinder block, a rotor, a partition plate, a working fluid inlet, a working fluid outlet, and a vane.
  • the rotor is disposed in the cylinder block, and the rotor and the cylinder block Forming an annular chamber, the partition partitioning the continuous cavity of the annular chamber, the working fluid inlet and the working fluid outlet are respectively located at two sides of the partition, and the vane is in a plane parallel to the axis of the cylinder or through the axis of the cylinder
  • the movably disposed inner portion is guided by the cam to pass over the partition, the cam being disposed concentrically with the rotor.
  • the blades may have at least two, and the two blades are symmetrically arranged around the above axis.
  • the partition may be in one of the near angle of repose and the far angle of repose of the cam, that is, the first angle of repose, and the other of the near angle of repose and the angle of repose of the angle, that is, the second angle of repose, is greater than
  • the adjacent two blades contain an angle between the thickness of the flesh, and the blade and the cam running in the second angle of repose are sealed with a low sub-moving surface, and output work during the rotation, and the thrust movement angle and the return movement angle of the cam
  • the inner moving blade is pushed away from the cavity wall of the annular chamber by the cam, and there is no pressure difference on both sides of the blade, and no work is performed.
  • the cam may be a disc cam with a stroke greater than or equal to the bore diameter in the radial direction of the annular chamber.
  • the cam may be a cylindrical cam with a stroke greater than or equal to the bore diameter in the axial direction of the annular chamber.
  • the cam can be a female cam and can be placed in the cylinder together with the partition.
  • the working inlet is located in the thrust movement angle
  • the working outlet is located in the return movement angle
  • the far rest angle is the working segment of the blade.
  • the cam can be a male cam and is placed on the rotor together with the partition.
  • the working inlet is located in the return movement angle, the working outlet is in the thrust movement angle, and the near rest angle is the work segment.
  • the cam may be a female cam
  • the female cam includes two thin plates disposed inside the annular chamber, the two thin plates are symmetrically distributed in the axial direction of the annular chamber, the two thin plates are connected to the partition plate, and the two thin plates are A cam is formed with an outer side wall of the annular chamber.
  • the cam may be a male cam
  • the male cam includes two thin plates disposed inside the annular chamber, the two thin plates are symmetrically distributed in the axial direction of the annular chamber, and the two thin plates are connected to the partition plate, and the two thin plates are connected.
  • a cam is formed with an inner side wall of the annular chamber.
  • the blades and cams can be closed in a force-tight manner, and the locking force can be provided by the spring force of the spring or the pressure of the compressed gas.
  • a guide groove may be disposed on one side wall of the annular chamber, and both sides of the blade moving direction are embedded in the guide groove.
  • the normal projection of the blade may be C-shaped, the thickness of the two legs on both sides of the moving direction being equal to the depth of the guiding groove [24]
  • the central axis of movement of the blade can be offset from the center of rotation of the cam.
  • the cam can be a soft cam.
  • the soft cam is composed of an angle control mechanism and an actuator.
  • the magnitude of the push motion angle and the return motion angle is equal to the product of the single stroke stroke and the rotor angular velocity of the actuator.
  • the first angle of repose is greater than the angle between the partition and the axis, and the second angle of repose is greater than the angle between the thickness of the adjacent two blades.
  • the present invention also provides a vane type continuous rotary cylinder including a cylinder block, a rotor, a partition plate, a working fluid inlet, a working fluid outlet, and a vane.
  • the rotor is disposed in the cylinder body, and a ring is formed between the rotor and the cylinder block.
  • the utility model further comprises a thin plate for guiding the blade over the partition plate, wherein the thin plate is disposed in the annular chamber and forms a side wall with a side wall on the outer circumference of the annular chamber, that is, a side wall of the inner circumferential direction of the cylinder body.
  • the present invention further provides a vane type continuous rotary cylinder, comprising a cylinder block, a rotor, a partition plate, a working fluid inlet, a working fluid outlet, and a vane.
  • the rotor is disposed in the cylinder body, and an annular cavity is formed between the rotor and the cylinder block.
  • the partition is fixedly connected to the rotor, and the continuous cavity of the annular chamber is partitioned, and the working fluid inlet and the working fluid outlet are provided by the rotor and respectively located on two sides of the partition, and the vane is disposed on the cylinder, and the characteristic is And a thin plate guiding the blade over the partition plate, wherein the thin plate is disposed in the annular chamber and forms a male cam, a male cam and a cylinder, with a side wall on the inner circumference of the annular chamber, that is, a side wall of the circumferential direction of the rotor
  • the body and the blade constitute a concentric cam mechanism; at least two blades are symmetrically disposed on the cylinder; the male cam is coaxial with the rotor; the partition is located within the distal angle of repose of the male cam, and the near-rest angle is greater than the adjacent two blades The angle between the angles includes the flesh thickness of the blade, the blade running in the near angle of repose and the male cam are sealed for the
  • the present invention further provides a vane type continuous rotary cylinder including a cylinder block, a rotor, a partition plate, a working fluid inlet, a working fluid outlet, and a vane.
  • the rotor is disposed in the cylinder body, and a ring is formed between the rotor and the cylinder block.
  • the utility model is characterized in that it further comprises a cylindrical cam extending from the cylinder body, at least two blades are symmetrically arranged on the rotor, the cylindrical cam is coaxial with the rotor, the rotor, the cam and the blade constitute a concentric cam mechanism; the partition plate is located at the cylindrical cam In the near-rest angle, the same angle of repose is greater than the angle between the adjacent two blades, the angle includes the flesh thickness of the blade, and the blade running in the far angle of repose is sealed with the cylindrical cam as a low side moving surface. And outputting work in rotation, the blade moving in the thrust movement angle and the return movement angle of the cylindrical cam is pushed away from the cavity wall of the annular chamber by the cylindrical cam, and there
  • the present invention also provides a vane type continuous rotary cylinder including a cylinder block, a rotor, a partition plate, a working fluid inlet, a working fluid outlet, and a vane.
  • the rotor is disposed in the cylinder body, and a ring is formed between the rotor and the cylinder block.
  • a chamber, the partition partitions the continuous cavity of the annular chamber, and the working fluid inlet and the working fluid outlet are respectively located on two sides of the partition, and the utility model further comprises: a swingable blade having an axis parallel to the rotor axis and The guide vane passes over the cam of the diaphragm that is concentric with the rotor.
  • FIG. 1 is a schematic diagram of the principle of a first embodiment of the present invention, in which fluid pressure energy is converted into mechanical energy.
  • FIG. 2 is a perspective view showing the structure of the cylinder shown in Fig. 1.
  • FIG. 3 is a schematic view showing the principle of forming a closed chamber during the movement of the embodiment shown in FIG. 1.
  • FIG. 4 is a schematic diagram of the principle of the first embodiment of the present invention, in which mechanical energy is converted into fluid pressure energy.
  • Figure 5 is a schematic diagram of the principle of the second embodiment of the present invention.
  • Figure 6 is a front cross-sectional view showing a third embodiment of the present invention, in which a cylindrical cam is located on a cylinder block.
  • Figure 7 is an exploded view of the embodiment of Figure 6.
  • Figure 8 is a front cross-sectional view showing a fourth embodiment of the present invention, taken along line A-A of Figure 9;
  • Figure 9 is a cross-sectional view taken along line B-B of Figure 8.
  • Figure 10 is a schematic view of the structure of the rotor of Figure 9.
  • Figure 11 is an exploded view of the embodiment of Figure 9.
  • FIG. 12 is a schematic diagram of a conventional single-blade swing cylinder.
  • Figure 13 is a front cross-sectional view showing a fifth embodiment of the present invention, taken along line A-A of Figure 14.
  • Figure 14 is a cross-sectional view taken along line C-C of Figure 13;
  • Figure 15 is a cross-sectional view taken along line B-B of Figure 14.
  • Figure 16 is a schematic diagram of the principle of the sixth embodiment of the present invention.
  • Female cam means a cam in which the follower is located, such as the cam of the first embodiment described below;
  • Machine cam means a cam on which the follower is located, such as the cam of the second embodiment described below.
  • the vane type continuous rotary cylinder of the present invention is similar in structure to a vane type swing cylinder, and includes a cylinder block 1, a rotor 2, a partition plate 3, a working fluid inlet 4, a working fluid outlet 5, and a cam. 6.
  • the blade 7, which is different from the existing blade type oscillating cylinder, has a plurality of cams 6, and the function of the cam 6 is to displace the working blade 7 in a plane parallel to or through the axis of the cylinder, and can pass over the partition 3, cycle work, to achieve a one-way continuous circular motion.
  • the rotor 2, the cam 6, and the vanes 7 constitute a concentric cam mechanism.
  • an annular chamber is provided by the cylinder 1 and the rotor 2, and a partition 3 is provided in the chamber, the working fluid inlet 4 and the working fluid outlet 5 is located on both sides of the partition plate 3.
  • the cam 6 is a disc-shaped cam, which is disposed inside the annular chamber and is composed of two sheets of the same shape and symmetrically distributed in the axial direction of the annular chamber and the thin plate 62 and the annular chamber.
  • the outer side wall in the circumferential direction i.e., the inner side wall of the cylinder 1 in the circumferential direction
  • the two sheets are symmetrically disposed for the purpose of applying a force balance at the axial ends of the vane 7, and in the two sheets Under the action of the grooves 67 and 68, the vanes 7 cannot separate the annular chambers to form pressure differences on both sides.
  • the center of rotation of the cam 6 coincides with the axis of the rotor 2, the stroke of which is greater than or equal to the bore diameter in the radial direction of the annular chamber, and the near rest angle 8 of the cam 6 is greater than or equal to the angle between the thickness of the partition 3 and the axis and the partition 3 is included Inside, the blades moving within this angle can completely avoid the partition 3 .
  • the push motion angle 10 and the return motion angle 11 are separated on both sides of the partition 3, the working fluid inlet 4 is included in the thrust movement angle 10, and the working fluid outlet 5 is included in the return movement angle 11, and the distal angle of return is 9
  • the corresponding profile coincides with the outer wall of the annular chamber.
  • the two vanes 7 are evenly symmetrically distributed around the circumference of the annular chamber, and the far angle of repose 9 of the cam 6 is larger than the angle between the two vanes 7 (and considering the influence of the thickness of the vane 7 on the angle and the possibility of a jump phenomenon influences) .
  • the annular chamber When only one blade 7 is within the far angle of repose 9, the annular chamber is divided into two chambers by the partition 3 and the vane 7, the inlet chamber 14 on the working inlet 4 side and the outlet chamber on the working outlet side. 15. When the two blades 7 are located within the distal angle of repose 11, the annular chamber is divided into three chambers, namely: an inlet chamber 14, an outlet chamber 15, and a closed chamber 16 (shown in Figure 3).
  • the working fluid inlet 4 is connected to the working fluid outlet 5, and there is no pressure difference on both sides of the vane 7. To maintain continuous rotation, it is only necessary to rely on inertia or multi-level misaligned series.
  • the output torque and output power are discontinuous, and the energy loss is too large, but continuous rotation can also be achieved.
  • cam 6 is a disc-type female cam
  • follower that is, the vane 7 moves inside the cam and the partition
  • the follower that is, the vane 7 moves outside the cam and is located at the rotor 2 ⁇ with the partition 3, as shown in FIG. 5, the vane 7 It is disposed on the cylinder block 1.
  • the near-rest angle 8 is interchanged with the far-away angle 9
  • the thrust angle 10 is interchanged with the return angle 11 in the outer wall of the annular chamber of the foregoing embodiment. In the example, it becomes the inner wall of the annular chamber, and the other contents are unchanged.
  • the cam 6 is a cylindrical cam and is located in the cylinder 1, and its operation principle can be understood by referring to the description of the first embodiment.
  • a cylindrical cam can also be disposed on the rotor 2, and the principle of operation can be understood with reference to the description of the first embodiment and the second embodiment.
  • the cams of the foregoing embodiments may be appropriately modified in combination with various techniques relating to cam mechanisms in modern mechanical technology, typically:
  • the blade 7 acts as a follower. When its mass is large, the momentum has a great influence on its motion.
  • the primary consideration is to reduce its maximum speed. When it is required for its inertial force, the primary consideration is It is to reduce its maximum acceleration; when its motion stability is higher, the primary consideration is its maximum jerk.
  • Convex contour design should be performed for five different applications, such as polynomial, harmonic, and cycloidal motion, or combined motion laws for different applications.
  • a suitable follower bias can reduce the pressure angle of the blade 7 and increase mechanical efficiency.
  • the disadvantage is that it is unable to operate in both directions, the processing difficulty is increased, and the common spring compression space cannot be realized.
  • the mechanism size is large, and it is suitable for the case where the pressure gas 13 is used as the closing force and the disc type positive cam design.
  • Soft cam system refers to the combination of components that make the follower perform the same function as the cam in circular motion, such as angle sensor + control mechanism + power output + actuator, power and actuator can be pneumatic or electric high-speed components .
  • Advantages of the soft cam system The follower has no wear and impact with the high movement of the cam, no pressure angle, and no biasing of the follower; Disadvantages: a. Due to the rapid reciprocating of the straight line, the two ends of the stroke of the actuating blade 7 are Impact, increased cushioning will prolong the operating time and reduce the mechanism speed; b. System failure ⁇ Blade 7 and diaphragm 3 have the risk of destructive impact; This system is suitable for high life and low speed of the mechanism.
  • the number of the blades 7 is four. Comparing FIG. 1 and FIG. 8, it can be found that by increasing the number of the blades 7, a large thrust movement angle 9 and a return movement angle 10 can be obtained.
  • the contour is smoother, which reduces the running impact and increases the speed.
  • the thrust movement angle 9 and the return movement angle 10 do not need to consider the sealing of the cylinder wall and the blade 7, and the processing difficulty is lowered and a large working fluid inlet 4 and a working fluid outlet 5 can be set.
  • the large working fluid inlet 4 corresponds to a large pressure chamber, and the fluid working fluid has small flow resistance and stable pressure. When applied to internal combustion engines, there is enough combustion space, sufficient combustion, low waste, and complete conversion of heat energy. No suction pressure for the stroke, the available fuel range is wide; large working fluid outlet 5 fast pressure relief, low residual pressure, help to improve the efficiency of the mechanism.
  • the radial projection of the rotor 2 is "" shaped, consisting of a rotating shaft 21 and two flanges.
  • the disk 22 is composed of two flanges 22, and the inner side of the two flanges 22 radially sandwiches the partition plate 3 to form two side walls of the annular chamber.
  • a guiding groove 220 is radially opened, and the guiding groove 220 penetrates the rotating shaft 21
  • the number of blades 7 is even, moving radially within the guide groove 220, each group of blades 7 sharing a compression space, using a pressurized gas to provide a closing force (as understood with reference to Figure 5), the pressurized gas being supplied through the axial bore.
  • the structure can withstand high internal pressure and has good sealing performance.
  • the arrangement of the same guiding groove 220 helps to reduce the size of the cylinder.
  • the crucible rotor 2 is preferably designed separately.
  • the blade 7 is normally projected into a C shape, and its two legs are buried in the guide groove 220, the thickness of which is equal to the depth of the guide groove 220, and the corresponding position on the cylinder block. Set to have a bit groove or step, this setting helps to increase the seal.
  • the end cover 22 provided outside the cylinder is provided with intake holes 18-1, 18-2, exhaust holes 19-1, 19-2, intake grooves 20-1, 20-2, and exhaust grooves 21- 1, 21-2, the inlet and exhaust holes on the end cover are respectively electrically connected to the inlet and exhaust grooves, and are connected to the intake and exhaust holes 17 on the rotor 2, and the foregoing structure is matched with an air pump to form an angle control mechanism.
  • the commutation of the intake and exhaust can be completed to control the actuation of the vane 7, and the function that the cam 6 can achieve is completed.
  • the angle control mechanism of the end cap 22 and the actuator on the rotor blade form a soft Cam system.
  • the soft cam system of the present embodiment is different from the cam 6 of the first embodiment in that there is no clear boundary between the near rest angle 8 and the return movement angle 11, the far rest angle 9 and the kick movement angle 10.
  • the magnitude of the push motion angle 10 and the return motion angle 11 is varied and is equal to the product of the turn of the actuator and the rotational angular velocity of the rotor 2 for the single stroke of the actuator.
  • the near angle of repose 8 includes the angle between the flesh thickness of the baffle 3 and the axis
  • the far angle of repose 9 is greater than the angle between the adjacent two vanes 7 including the thickness of the flesh
  • the soft cam system can also be used in disc cam or cylindrical cam mechanisms.
  • the soft cam system shown above is just one of the ways. It can be implemented in a variety of ways, but both have an angle control mechanism and an actuator.
  • the rotor 2 of the present embodiment has a flange at the same end.
  • the pin shafts of the oscillating vanes 7 are respectively fixed on the holes on the two flanges and are sealed, except that the vanes 7 are in a swinging manner, and the flanges are not provided with guide grooves.
  • the first embodiment and the fourth embodiment use a disc type female cam, and the structural features are: simple and compact structure, easy processing, good sealing, and a large working fluid inlet 4 and a working fluid outlet 5 can be provided.
  • the second embodiment uses a disc-type male cam structure, as shown in FIG. 5, the characteristics of the disc-type male cam structure.
  • the third embodiment uses a cylindrical cam mechanism, as shown in Fig. 6, Fig. 7, the structural characteristics of the cylindrical cam mechanism are: complicated structure, high cam processing, not suitable for the blade 7 biasing structure, suitable for spring to provide closure For occasions suitable for soft cam applications, suitable for applications where the ratio of circumference to length of the mechanism is small, suitable for cam and vane type closed structures.
  • the fifth embodiment uses a soft cam mechanism which can be separately combined with the foregoing embodiment, and the characteristics of the soft cam will be completely inherited.
  • the sixth embodiment uses a swinging vane mechanism, and its structural features are: high processing difficulty, only applicable to a disc type male cam or a disc type female cam mechanism, which can only be used for one-way operation, but the swing follower mechanism
  • the advantage of the setting is that, in the case of inheriting the advantages of the aforementioned disc cam, it also has the characteristics of small rigidity impact, good sealing, and suitable for high-speed sports occasions.
  • the present invention has been described with reference to the present embodiments, it will be understood by those skilled in the art that In the broadest sense, it is not intended to depart from the invention.
  • the two blades shown in FIG. 1 may be offset by a certain distance without being on the same straight line passing through the center of the rotor.
  • the center axis of rotation is offset from the center of rotation of the cam 6. Therefore, it is intended that the modifications and variations of the embodiments described above fall within the scope of the appended claims.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Rotary Pumps (AREA)

Abstract

L'invention concerne un cylindre rotatif continu de type à ailettes comprenant un corps de cylindre (1), un rotor (2), un déflecteur (3), un orifice d'entrée de fluide de travail (4), un orifice de sortie de fluide de travail (5) et des ailettes (7) ; le rotor (2) étant disposé à l'intérieur du corps de cylindre (1) ; une chambre annulaire étant formée entre le rotor (2) et le corps de cylindre (1) ; le déflecteur (3) séparant la cavité continue de la chambre annulaire ; l'orifice d'entrée de fluide de travail (4) et l'orifice de sortie de fluide de travail (5) étant situés respectivement sur les deux côtés du déflecteur (3). Le cylindre rotatif continu de type à ailettes selon l'invention comprend également une came (6) disposée de façon concentrique avec le rotor (2) pour guider les ailettes (7) pour traverser le déflecteur (3). Les ailettes du cylindre rotatif tournent de façon continue, ce qui améliore l'efficacité.
PCT/CN2009/072971 2009-04-20 2009-07-29 Cylindre rotatif continu de type a ailettes WO2010121450A1 (fr)

Applications Claiming Priority (2)

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CNA2009100496044A CN101586474A (zh) 2009-04-20 2009-04-20 叶片式连续旋转缸
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CN109854499A (zh) * 2019-04-01 2019-06-07 杨金牛 多功能高压泵

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